US20150256911A1 - Elastomeric Torsion Bushings for Levered Loudspeakers - Google Patents
Elastomeric Torsion Bushings for Levered Loudspeakers Download PDFInfo
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- US20150256911A1 US20150256911A1 US14/200,614 US201414200614A US2015256911A1 US 20150256911 A1 US20150256911 A1 US 20150256911A1 US 201414200614 A US201414200614 A US 201414200614A US 2015256911 A1 US2015256911 A1 US 2015256911A1
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- United States
- Prior art keywords
- loudspeaker
- lever
- elastomeric
- acoustic diaphragm
- taper angle
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
- H04R1/00—Details of transducers, loudspeakers or microphones
- H04R1/02—Casings; Cabinets ; Supports therefor; Mountings therein
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- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
- H04R11/00—Transducers of moving-armature or moving-core type
- H04R11/02—Loudspeakers
-
- H—ELECTRICITY
- H04—ELECTRIC COMMUNICATION TECHNIQUE
- H04R—LOUDSPEAKERS, MICROPHONES, GRAMOPHONE PICK-UPS OR LIKE ACOUSTIC ELECTROMECHANICAL TRANSDUCERS; DEAF-AID SETS; PUBLIC ADDRESS SYSTEMS
- H04R7/00—Diaphragms for electromechanical transducers; Cones
- H04R7/16—Mounting or tensioning of diaphragms or cones
Definitions
- This disclosure relates to elastomeric torsion bushings, and more particularly to elastomeric torsion bushings which provide pivots for lever arms used to drive motion of acoustic diaphragms in loudspeakers.
- This disclosure is based, in part, on the realization that elastomeric torsion bushings can be utilized to provide pivots for lever arms used to drive motion of acoustic diaphragms in loudspeakers.
- the use of such bushings in this manner can provide a low cost method for forming the pivot.
- Such bushings can also exhibit high radial and/or axial stiffness, which can be beneficial for resisting radial and/or axial crashing forces.
- a loudspeaker in one aspect, includes an acoustic diaphragm, an oscillatory force source, a lever coupling the oscillatory force source to the acoustic diaphragm, and a pivot coupled to the lever such that the lever moves in an arcuate path about the pivot when the oscillatory force source applies a force to the lever.
- the pivot includes at least one torsion bushing.
- the at least one torsion bushing includes a first member, a second member coupled to the lever and movable relative to the first member, and an elastomeric member coupling the first member to the second member.
- Implementations may include one of the following features, or any combination thereof.
- the elastomeric member is formed of an elastomer such as silicone rubber or polyurethane.
- a first surface of the elastomeric member is bonded to the first member, and a second surface of the elastomeric member is bonded to the second member such that the second surface moves with the second member relative to the first surface.
- the elastomeric member is formed between the first and second members in a mold-in-place process.
- the elastomeric member is bonded to the first member and the second member with an adhesive.
- the elastomeric member is in the form of a frusto-cone having a hollow center region.
- the frusto-cone has an outer diameter that tapers at a first taper angle along the length of the frusto-cone and an inner diameter that tapers at a second taper angle along the length of the hollow center region.
- the second member includes a tapered recess within which the elastomer is disposed. The tapered recess tapers at the first taper angle, and the first member includes a tapered portion that tapers at the second taper angle.
- the second taper angle is smaller than the first taper angle such that the elastomeric member has a substantially constant thickness ratio (e.g., about 1.2 to about 3) along the length of the hollow center region, wherein the thickness ratio is the ratio of the outer diameter to the inner diameter.
- a substantially constant thickness ratio e.g., about 1.2 to about 3
- the elastomeric member is in the form of a hollow cylinder having a thickness ratio of about 1.2 to about 3, wherein the thickness ratio is the ratio of an outer diameter of the hollow cylinder to an inner diameter of the hollow cylinder.
- the elastomeric member includes a plurality of elastomeric ribs each having a first end connected to the first member and a second end connected to the second member.
- the loudspeaker includes an enclosure, and a surround that connects the acoustic diaphragm to the enclosure.
- the first member can be fixed in position relative to the enclosure.
- At least one end of the first member is secured to the enclosure.
- the surround is mounted to a frame and the frame is connected to the enclosure, and at least one end of the first member is secured to the enclosure via the frame.
- the oscillatory force source includes a moving magnet motor.
- the moving magnet motor includes an armature that is coupled to the lever and includes a permanent magnet, and a stator for creating magnetic flux for the armature to interact with, thereby to drive motion of the acoustic diaphragm.
- the moving magnet motor is arranged such that magnetic crashing forces resulting from magnetic attraction between the stator and the one or more permanent magnets are substantially parallel to an axis of rotation of the lever.
- the moving magnet motor is arranged such that magnetic crashing forces resulting from magnetic attraction between the stator and the one or more permanent magnets are substantially perpendicular to an axis of rotation of the lever.
- a loudspeaker in another aspect, includes an acoustic diaphragm and a moving magnet motor.
- the moving magnet motor includes an armature comprising a permanent magnet, and a stator for creating magnetic flux for the armature to interact with, thereby to drive motion of the armature.
- the loudspeaker also includes a lever that couples the armature and the acoustic diaphragm to transmit motion of the armature to the acoustic diaphragm to cause the acoustic diaphragm to move, and a pivot that is coupled to lever so that motion of the armature causes the lever to move in an arcuate path about the pivot.
- the pivot includes a pair of elastomeric torsion bushings. Each of the elastomeric torsion bushings includes a first member, a second member that is coupled to the lever and is movable relative to the first member, and an elastomeric member that couples the first member to the second member.
- Implementations may include one of the following features, or any combination thereof.
- the elastomeric torsion bushings are spaced apart so as to allow the acoustic diaphragm to move therebetween.
- Implementations can provide one or more of the following advantages.
- the use of one or more elastomeric torsion bushings provide for a frictionless pivot for a lever arm used to drive motion of acoustic diaphragm.
- the use of one or more elastomeric torsion bushings provides for a pivot that has low torsional stiffness (e.g., 0.1-1 Nm/rad).
- the use of one or more elastomeric torsion bushings provides for a pivot that has high radial stiffness (e.g., 200-2000 N/mm) and/or high axial stiffness (50-500 N/mm).
- FIG. 1A is a top plan view of a loudspeaker that employs an elastomeric torsion bushing for providing a pivot for a lever that drives an acoustic diaphragm.
- FIG. 1B is a cross-sectional side view of the loudspeaker of FIG. 1A , taken along line 1 B- 1 B.
- FIG. 2 illustrates oscillatory, arcuate movement of the lever and pistonic movement of an acoustic diaphragm of the loudspeaker of FIG. 1A .
- FIG. 3A is a top view of the pivot and lever of FIG. 1A .
- FIG. 3B is a cross-sectional view of the pivot of FIG. 3A , taken along line 3 B- 3 B.
- FIG. 3C is a cross-sectional view of the pivot and lever of FIG. 3A , taken along line 3 C- 3 C.
- FIG. 4 is a perspective view of the pivot and lever of FIG. 1A including an armature for a moving magnet motor.
- FIG. 5 is a perspective view of a stator for a moving magnet motor.
- FIGS. 6A , 6 B, and 6 C are top, end, and side views, respectively, of the pivot and lever of FIG. 1A together with a moving magnet motor.
- FIG. 7A is a top view of the lever of FIG. 1A with an alternative pivot arrangement.
- FIG. 7B is a cross-sectional side view of an elastomeric torsion bushing from the pivot of FIG. 7A , taken along line 7 B- 7 B.
- FIG. 8A is a top plan view of another implementation of a loudspeaker that employs elastomeric torsion bushings for providing a pivot for a lever that drives an acoustic diaphragm.
- FIG. 8B is a cross-sectional side view of the loudspeaker of FIG. 8A , taken along line 8 B- 8 B.
- FIG. 9 illustrates oscillatory, arcuate movement of the lever and pistonic movement of an acoustic diaphragm of the loudspeaker of FIG. 8A .
- FIGS. 10 and 11 are end views of alternative implementations of elastomeric torsion bushings.
- FIGS. 12A and 12B are plan and perspective views, respectively, of a multi-lever loudspeaker.
- FIG. 12C is an exploded perspective view of the levers from the loudspeaker of FIG. 12A showing details of elastomeric torsion bushings.
- FIGS. 13A and 13B are plan and perspective views, respectively, of another implementation of a multi-lever loudspeaker.
- FIG. 13C is an exploded perspective view of the levers from the loudspeaker of FIG. 13A showing details of elastomeric torsion bushings.
- loudspeaker 100 includes an acoustic diaphragm 102 (e.g., a cone type speaker diaphragm, also known simply as a “cone”) that is mounted to an enclosure 104 , which may be metal, plastic, or other suitable material, by a surround 106 , which functions as a pneumatic seal and as a suspension element.
- a surround 106 which functions as a pneumatic seal and as a suspension element.
- the surround 106 is mounted to a frame 108 and the frame 108 is connected to the enclosure 104 .
- the loudspeaker 100 includes a lever 110 that is mechanically connected at one point along the lever 110 to the acoustic diaphragm 102 and at another point along the lever 110 to an oscillatory force source 112 .
- the lever 110 is pivotally connected to a mechanical ground reference, such as the enclosure 104 or the frame 108 , via a pivot 114 .
- a mechanical ground reference such as the enclosure 104 or the frame 108
- the lever 110 is driven in an arcuate path (arrow 117 ) about the pivot 114 .
- the motion of the lever 110 is transferred to the acoustic diaphragm 102 via the connection point, which causes the acoustic diaphragm 102 to move along a path (arrow 118 ) between a fully extended position and a fully retracted position.
- connection point may include a connector 119 , such as a hinge or link, which allows the lever 110 to move relative to the acoustic diaphragm 102 , thereby to allow the acoustic diaphragm 102 to move in a pistonic motion (arrow 118 ), rather than following the arcuate path of the lever 110 .
- a connector 119 such as a hinge or link
- the pivot 114 includes at least one elastomeric torsion bushing.
- FIGS. 3A , 3 B, and 3 C illustrate one implementation of the pivot 114 which includes such an elastomeric torsion bushing 120 .
- the elastomeric torsion bushing 120 provides a low cost, frictionless hinge for the lever 110 .
- the bushing 120 includes a first, outer (housing) member 122 ; a second, inner (pin) member 124 ; and an elastomeric member 126 disposed therebetween.
- a first, inner surface 128 of the elastomeric member 126 is bonded to the inner member 124 and a second, outer surface 130 of the elastomeric member 126 is bonded to the outer member 122 such that the outer surface 130 of the elastomeric member 126 moves with the outer member 122 , during rotation of the lever 110 , relative to the inner surface 128 .
- At least one of the opposing ends 136 a , 136 b of the inner member 124 is fixed to a mechanical ground reference, such as the enclosure 104 ( FIG.
- the outer member 122 is coaxial with the inner member 124 and is secured to the lever 110 such that the outer member 122 rotates with the lever 110 relative to the inner member 124 .
- the lever 110 and the outer member 122 may both be part of one unitary structure.
- the outer and inner members 122 , 124 can be formed of a metal, such as steel, or other suitable high stiffness material (e.g., plastics).
- the elastomeric member 126 is formed of an elastomer, such as silicone rubber, polyurethane, etc. Silicone materials may be beneficial because they tend to exhibit very good properties of creep. Silicone rubber, for example, can offer several material property benefits, such as temperature stability; low modulus; low, moderate, or high dissipation factor (tan ⁇ ) is possible; good creep resistance; fast curing using catalysts and elevated temperatures; injection moldable; and can offer very high elongation (e.g., about 900%).
- the elastomeric member 126 can be formed between the outer and inner members 122 , 124 using a mold-in-place process, which provides sufficiently high strength bonding between the elastomeric member 126 and the outer and inner members 122 , 124 and which allows the parts to be of lower tolerance since the elastomeric member 126 forms to the shape of the space between the outer and inner members 122 , 124 .
- the parts could be formed (e.g., molded and/or machined) separately and then bonded together using an adhesive.
- the outer member 122 , the inner member 124 , and the elastomeric member 126 could be connected together using geometric locking.
- ⁇ angle of rotation (in radians) of the outer surface of the elastomeric member relative to the inner surface of the elastomeric member.
- a thickness ratio “t” of about 1.2 to about 3 generally provides a bushing with sufficiently low peak torsional strain (e.g., less than 20%) and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm).
- Equations (1) and (2) also show that the stiffness ratios improve when the inner diameter “a” of the elastomeric member 126 is minimized.
- Those limits include: stiffness of the inner member 124 , and shear forces between the elastomeric member 126 and the inner member 124 .
- stiffness of the inner member 124 As the inner diameter “a” is reduced the shearing load resulting from the rotation of the outer member 122 relative to the inner member 124 acts on a diminishing surface area.
- the inner diameter “a” needs to be large enough to provide sufficient surface area so that the shearing load does not exceed the strength of the bond between the elastomeric member 126 and the inner member 124 .
- FIGS. 4 , 5 , 6 A, 6 B and 6 C illustrate one implementation of the oscillatory force source 112 ( FIG. 6A ) for applying force to the lever 110 .
- the oscillatory force source 112 includes a substantially planar armature 142 that is attached to the lever 110 .
- the armature 142 includes one or more permanent magnets 146 (one shown).
- the armature 142 and the lever 110 may be part of one unitary structure.
- the oscillatory force source 112 also includes a stator 148 that includes one or more cores 150 (two shown) which define an air gap 152 .
- the cores 150 are formed of high magnetic permeability material around which coils 154 are wound.
- the lever 110 is positioned such that the armature 142 is in the air gap 152 and electrical current is passed through the coils so that that the combination of the armature 142 , the cores 150 , and the coils 154 form a moving magnet motor.
- the force results from the interaction of the magnetic field in the gap due to the current flowing in the coils 154 and the magnetic field of the permanent magnet 146 , so the force is applied to the lever 110 in a non-contact manner.
- Moving magnet motors can be subject to a magnetic crashing force which results from magnetic attraction between the stator 148 and armature 142 .
- the crashing force is substantially in the axial direction, and varies as a function of the distance between the armature 142 and the cores 150 ; the closer the permanent magnet 146 is to the cores 150 , the stronger the magnetic crashing force. It may be convenient to think of the structure as requiring a crashing stiffness that inhibits the armature 142 from crashing into the cores 150 .
- the high axial stiffness of the elastomeric torsion bushing 120 can be beneficial to ensure that there is little relative motion between the armature 142 and the cores 150 in the axial direction (as shown in FIGS. 6A and 6B ).
- FIGS. 7A and 7B illustrate another implementation of a pivot 214 that can be employed, for example, in the loudspeaker 100 of FIG. 1A and which may be particularly beneficial where the magnetic crashing forces are high in the axial direction.
- the pivot 214 includes a pair of conical elastomeric torsion bushings 220 arranged along the axis of rotation 140 of the lever 110 with a shaft member 221 extending therebetween.
- Each elastomeric torsion bushing 220 includes a first, outer (housing) member 222 ; a second, inner (pin) member 224 ; and an elastomeric member 226 disposed therebetween and bonded thereto.
- a first end 236 a of the inner member 224 is fixed to a mechanical ground reference, such as the enclosure 104 ( FIG. 1A ) or the frame 108 ( FIG. 1A ) and such that a longitudinal axis 238 of the inner member 224 is coincident with the axis of rotation 140 of the lever 110 .
- the outer member 222 is coaxial with the inner member 224 and is secured to the lever 110 such that the outer member 222 rotates with the lever 110 relative to the inner member 224 .
- a first (inner) surface 228 of the elastomeric member 226 is bonded to the inner member 224 and a second (outer) surface 230 of the elastomeric member 226 is bonded to the outer member 222 such that the second surface 230 moves with the outer member 222 (e.g., during rotation of the lever) relative to the inner surface 228 .
- the lever 110 and the outer member 222 may both be part of one unitary structure.
- the outer members 222 can be integral with the shaft member 221 , which can be integral with the lever 110 .
- the elastomeric member 226 is in the form of frusto-cone having a hollow center region 260 .
- the frusto-cone has an outer diameter “b” that tapers at a first taper angle ⁇ along the length of the frusto-cone and an inner diameter “a” that tapers at a second taper angle ⁇ along the length of the hollow center region 260 .
- the first and second taper angles ⁇ , ⁇ differ, with the second taper angle ⁇ being smaller than the first taper angle ⁇ , so as to maintain a substantially constant thickness ratio “t” of the elastomeric member 226 along the length of the hollow center region 260 .
- the thickness ratio “t” is the ratio of the outer diameter “b” over the inner diameter ‘a.’ It has been found that a thickness ratio “t” of about 1.2 to about 3 generally provides a bushing with sufficiently low peak strain and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm).
- the outer member 222 includes a tapered recess 262 within which the elastomeric member 226 is disposed.
- the tapered recess 262 tapers at the first taper angle ⁇ so that the outer surface 230 of the elastomeric member 226 conforms to the shape of the tapered recess 262 allowing for an intimate bond between the elastomeric member 226 and the outer member 222 .
- the inner member 224 includes a tapered end portion 264 that is received within the hollow center region 260 of the elastomeric member 226 .
- the tapered end portion 264 tapers at the second taper angle ⁇ so that the inner surface 228 of the elastomeric member 226 conforms to the shape of the tapered end portion 264 allowing for an intimate bond between the elastomeric member 226 and the inner member 224 .
- the introduction of these tapered surfaces along the axial direction of the pivot 214 allow for compression of the elastomeric member 226 between the tapered surfaces of the outer and inner members 222 , 224 in the axial direction.
- the compression of the elastomeric member 226 can assist the shear strength of the bonds between the elastomeric member 226 and the outer and inner members 222 , 224 in resisting magnetic crashing forces in the axial direction.
- FIGS. 8A and 8B illustrate another example of a loudspeaker 300 that includes an acoustic diaphragm 302 that is mounted to an enclosure 304 by a surround 306 .
- the surround 306 is mounted to a frame 308 and the frame 308 is connected to the enclosure 304 .
- a lever 310 couples an armature 342 to the acoustic diaphragm 302 for transmitting motion of the armature 342 to the acoustic diaphragm 302 .
- the armature 342 includes one or more permanent magnets 346 (one shown, FIG. 8B ).
- the armature 342 is driven by a stator 348 , which provides a magnetic flux for the one or more permanent magnets 346 to interact with, thereby to drive motion of the acoustic diaphragm.
- the stator 348 that includes one or more cores 350 (two shown) which define an air gap 352 .
- the cores 350 are formed of high magnetic permeability material around which coils 354 are wound.
- the lever 310 is positioned such that the armature 342 is in the air gap 352 and electrical current is passed through the coils so that that the combination of the armature 342 , the cores 350 , and the coils 354 form a moving magnet motor 312 .
- the force results from the interaction of the magnetic field in the gap due to the current flowing in the coils 354 and the magnetic field of the permanent magnet 346 , so the force is applied to the lever 310 in a non-contact manner.
- the lever 310 is pivotally connected to a mechanical ground reference, such as the enclosure 304 or the frame 308 of the loudspeaker 300 , at a pivot 314 such that the lever 310 moves in an arcuate path.
- the lever 310 includes a pair of support arms 360 that are fixed to the pivot 314 and support the armature 342 .
- a cross-member 362 connects the support arms 360 to a lever arm 364 .
- the lever arm 364 is connected to the acoustic diaphragm 302 via a connector 319 , such as a hinge, which allows the lever 310 to move relative to the acoustic diaphragm 302 , thereby to allow the acoustic diaphragm 302 to move in a pistonic motion, rather than following the arcuate path of the lever 310 .
- a connector 319 such as a hinge
- the pivot 314 includes a pair of elastomeric torsion bushings 320 which are connected to each other via the cross-member 362 of the lever 310 .
- each of the bushings 320 includes an inner (pin) member 324 that includes a first end 336 a that is fixed to a mechanical ground reference, such as the enclosure 304 or the frame 308 of the loudspeaker 300 ; and a second, free end 336 b opposite the first end 336 a .
- An elastomeric member 326 circumferentially surrounds and is bonded to the inner member 324 .
- An outer (housing) member 322 circumferentially surrounds and is bonded to the elastomeric member 326 .
- the elastomeric member 326 is formed of an elastomer and can have a thickness ratio “t” of about 1.2 to about 3.
- the lever 310 in combination with the interaction between the armature 342 and the stator 348 (not shown in FIG. 9 ), moves the acoustic diaphragm 302 in a pistonic motion (as indicated by arrow 318 ).
- the bushings 320 are spaced apart from each other and the cross-member 362 ( FIG. 8A ) is offset from the bushings 320 such that the diaphragm is free to move therebetween, e.g., during a retraction.
- the moving magnet motor is arranged such that magnetic crashing forces resulting from interaction between the stator and the one or more permanent magnets 346 are substantially in the radial direction and perpendicular to the axis of rotation of the lever.
- the high radial stiffness offered by the elastomeric torsion bushings 320 can be particularly beneficial to inhibit crashing.
- a frusto-cone bushing such as illustrated in FIG. 7B , may also be used with the motor implementation of FIGS. 8A and 8B .
- FIG. 10 illustrates another implementation of an elastomeric torsion bushing 420 that can be utilized, for example, in the pivots in the loudspeakers described above.
- the bushing 420 includes a pivot shaft 424 .
- a plurality of elastomeric ribs 426 connect the pivot shaft 424 to a rigid housing 422 such that the rigid housing 422 can rotate relative to the pivot shaft 424 .
- Each of the ribs 426 includes a first end that is bonded to the pivot shaft 424 and a second end that is bonded to and moves with the rigid housing 422 .
- the pivot shaft 424 can have at least one of its ends fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and the rigid housing 422 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker.
- a mechanical ground reference such as an enclosure or a frame of a loudspeaker
- the rigid housing 422 can be fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and the pivot shaft 424 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker.
- a mechanical ground reference such as an enclosure or a frame of a loudspeaker
- FIG. 11 illustrate yet another implementation of an elastomeric torsion bushing 520 that can be utilized in the pivots of the loudspeakers described above.
- the bushing 520 includes a pivot shaft 524 .
- a pair of elastomeric ribs 526 connects the pivot shaft 524 to a rigid housing 522 .
- the pivot shaft 524 can have at least one of its ends fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and the rigid housing 522 can be secured to a lever used for driving an acoustic diaphragm of a loudspeaker.
- the rigid housing 522 can rotate relative to the pivot shaft 524 .
- Each of the ribs 526 includes a first end that is bonded to the pivot shaft 524 and a second end that is bonded to and moves with the rigid housing 522 .
- the housing 522 only partially surrounds the pivot shaft 524 .
- the rigid housing 522 can be fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and the pivot shaft 524 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker.
- a mechanical ground reference such as an enclosure or a frame of a loudspeaker
- the oscillatory force may instead be applied with a moving coil motor in which a coil wound on a bobbin moves with the lever.
- the motor also includes a stationary permanent magnet and a stator defining an air gap, in which the bobbin moves. Electrical current is passed through the coil so that that the combination of the magnet, core, and coil form a moving coil motor. Force results from interaction of a magnetic field due to the current flowing in the coil and a magnetic field from the stationary permanent magnet so the force is applied to the lever in a non-contact manner.
- the oscillatory force may be applied mechanically, for example, by connecting the lever to a linear actuator.
- FIGS. 12A and 12B are plan and perspective views, respectively, of an implementation of a loudspeaker 600 that includes plural levers 610 (two shown).
- FIG. 12C is an exploded perspective view of the levers 610 from the loudspeaker of FIG. 12A showing the details of the pivots 620 .
- the levers 610 are configured to rotate about respective pivots 614 .
- the pivots 614 are arranged inboard of a pair of armatures 642 , each of the armatures 642 being associated with a corresponding one of the levers 610 .
- an acoustic diaphragm 602 is mounted to an frame 608 by a surround 606 .
- the surround 606 is mounted to the frame 608 and the frame 208 can be connected to an enclosure (not shown).
- the levers 610 couple the armatures 642 to the acoustic diaphragm 602 for transmitting motions of the armatures 642 to the acoustic diaphragm 602 .
- Each of the armatures 642 includes a permanent magnet 646 ( FIG. 12C ), and each armature 642 is driven by an associated stator 648 .
- the stators 648 provide magnetic flux for the permanent magnets 646 to interact with, thereby to drive motion of the acoustic diaphragm 602 .
- Each of the stators 648 includes a pair of cores 650 , which together define an air gap within which an associated one of the armatures 642 is disposed.
- the cores 650 can be secured to the frame 608 (e.g., with an adhesive).
- Each core 650 includes a coil 654 of electrically conductive material wound about it. Current in coils 654 produce magnetic flux across the air gaps. The magnetic flux interacts with the permanent magnets 646 of the armatures 642 to drive the motion of the acoustic diaphragm 602 .
- Each lever 610 includes a pair of support arms 660 that support the armature 642 .
- a cross-member 662 connects the support arms 660 to a lever arm 664 .
- Each lever arm 664 is connected to the acoustic diaphragm 602 via connector 619 , such as a hinge or flexure, which allows the levers 610 to move relative to the acoustic diaphragm 602 , thereby to allow the acoustic diaphragm 602 to move in a pistonic motion, rather than following the arcuate path of the levers 610 .
- each of the bushings 620 includes an inner (pin) member 624 that includes a first end 636 a that is fixed to a mechanical ground reference, such as the frame 608 of the loudspeaker 600 ; and a second, free end 636 b opposite the first end 636 a .
- An elastomeric member 626 circumferentially surrounds and is bonded to the inner member 624 .
- FIGS. 13A , 13 B, and 13 C illustrate another implementation of a multi-lever loudspeaker that utilizes the conical elastomeric torsion bushings of FIG. 7A . Referring to FIGS.
- the loudspeaker 700 includes a mechanical load, in this example an acoustic diaphragm 702 (e.g., a cone type speaker diaphragm, also known simply as a “cone”), that is mounted to a frame 708 via a surround 706 .
- the frame 608 may be secured to an enclosure (not shown).
- the loudspeaker 700 also includes a pair of levers 710 each of which couples an associated armature 742 to the acoustic diaphragm 602 for transmitting motion of the armatures 742 to the acoustic diaphragm 602 to cause the acoustic diaphragm 602 to move, relative to the frame 708 .
- both of the armatures 742 are driven by a single, common stator 748 , which provides a magnetic flux for the permanent magnets 746 ( FIG. 13C ) of both of the armatures 742 to interact with, thereby to drive motion of the acoustic diaphragm 702 .
- the stator 748 can include a pair of U-shapes cores 750 of high magnetic permeability material, such as soft iron.
- Each core 750 includes a coil 754 of electrically conductive material wound about it.
- the cores 750 are arranged adjacent to each other and define an air gap therebetween, which is substantially filled by the armatures 742 .
- the air gap is a single, common air gap that is shared by both armatures 742 .
- Each of the levers 710 is pivotally connected to a mechanical ground reference, such as the frame 108 of the loudspeaker 100 , such that the levers 710 each move in an arcuate path about respective pivots 714 .
- the armatures 742 and the stator 748 are positioned beneath the acoustic diaphragm 702 with the pivots 714 being arranged outboard of the armatures 742 . That is, the armatures 742 are disposed between the pivots 714 of the levers 710 .
- the pivots 714 each include a pair of conical elastomeric torsion bushings 720 arranged along the axis of rotation of the associated lever 710 with a shaft member 721 extending therebetween.
- Each elastomeric torsion bushing 720 includes a first, outer (housing) member 722 ; a second, inner (pin) member 724 ; and an elastomeric member 726 disposed therebetween and bonded thereto.
- a first end of the inner member 724 is fixed to a mechanical ground reference, such as the frame 708 ( FIG. 13A ) and such that a longitudinal axis of the inner member 724 is coincident with the axis of rotation of the lever 710 .
- the outer member 722 is coaxial with the inner member 724 and is secured to the lever 710 such that the outer member 722 rotates with the lever 710 relative to the inner member 724 .
- a first (inner) surface 728 of the elastomeric member 726 is bonded to the inner member 724 and a second (outer) surface 730 of the elastomeric member 726 is bonded to the outer member 722 such that the second surface 730 moves with the outer member 722 (e.g., during rotation of the lever) relative to the inner surface 728 .
- the lever 710 and the outer member 722 may both be part of one unitary structure.
- the outer members 722 can be integral with the shaft member 721 , which can be integral with the lever 710 .
- the elastomeric member 726 is in the form of frusto-cone having a hollow center region 760 .
- the frusto-cone has an outer diameter “b” that tapers at a first taper angle along the length of the frusto-cone and an inner diameter “a” that tapers at a second taper angle along the length of the hollow center region 760 .
- the first and second taper angles differ, with the second taper angle being smaller than the first taper angle, so as to maintain a substantially constant thickness ratio “t” of the elastomeric member 726 along the length of the hollow center region 760 .
- the thickness ratio “t” is the ratio of the outer diameter “b” over the inner diameter “a.” It has been found that a thickness ratio “t” of about 1.2 to about 3 generally provides a bushing with sufficiently low peak strain and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm).
- the outer member 722 includes a tapered recess 762 within which the elastomeric member 726 is disposed.
- the tapered recess 762 tapers at the first taper angle ⁇ so that the outer surface 730 of the elastomeric member 726 conforms to the shape of the tapered recess 762 allowing for an intimate bond between the elastomeric member 726 and the outer member 722 .
- the inner member 724 includes a tapered end portion 764 that is received within the hollow center region 760 of the elastomeric member 726 .
- the tapered end portion 764 tapers at the second taper angle so that the inner surface 728 of the elastomeric member 726 conforms to the shape of the tapered end portion 764 allowing for an intimate bond between the elastomeric member 726 and the inner member 724 .
- the introduction of these tapered surfaces along the axial direction of the pivot 714 allow for compression of the elastomeric member 726 between the tapered surfaces of the outer and inner members 722 , 724 in the axial direction.
- the compression of the elastomeric member 726 can assist the shear strength of the bonds between the elastomeric member 726 and the outer and inner members 722 , 724 in resisting magnetic crashing forces in the axial direction.
Abstract
Description
- This disclosure relates to elastomeric torsion bushings, and more particularly to elastomeric torsion bushings which provide pivots for lever arms used to drive motion of acoustic diaphragms in loudspeakers.
- This disclosure is based, in part, on the realization that elastomeric torsion bushings can be utilized to provide pivots for lever arms used to drive motion of acoustic diaphragms in loudspeakers. The use of such bushings in this manner can provide a low cost method for forming the pivot. Such bushings can also exhibit high radial and/or axial stiffness, which can be beneficial for resisting radial and/or axial crashing forces.
- In one aspect, a loudspeaker includes an acoustic diaphragm, an oscillatory force source, a lever coupling the oscillatory force source to the acoustic diaphragm, and a pivot coupled to the lever such that the lever moves in an arcuate path about the pivot when the oscillatory force source applies a force to the lever. The pivot includes at least one torsion bushing. The at least one torsion bushing includes a first member, a second member coupled to the lever and movable relative to the first member, and an elastomeric member coupling the first member to the second member.
- Implementations may include one of the following features, or any combination thereof.
- In some implementations, the elastomeric member is formed of an elastomer such as silicone rubber or polyurethane.
- In certain implementations, a first surface of the elastomeric member is bonded to the first member, and a second surface of the elastomeric member is bonded to the second member such that the second surface moves with the second member relative to the first surface.
- In some implementations, the elastomeric member is formed between the first and second members in a mold-in-place process.
- In certain implementations, the elastomeric member is bonded to the first member and the second member with an adhesive.
- In some implementations, the elastomeric member is in the form of a frusto-cone having a hollow center region. The frusto-cone has an outer diameter that tapers at a first taper angle along the length of the frusto-cone and an inner diameter that tapers at a second taper angle along the length of the hollow center region. The second member includes a tapered recess within which the elastomer is disposed. The tapered recess tapers at the first taper angle, and the first member includes a tapered portion that tapers at the second taper angle.
- In certain implementations, the second taper angle is smaller than the first taper angle such that the elastomeric member has a substantially constant thickness ratio (e.g., about 1.2 to about 3) along the length of the hollow center region, wherein the thickness ratio is the ratio of the outer diameter to the inner diameter.
- In certain implementations, the elastomeric member is in the form of a hollow cylinder having a thickness ratio of about 1.2 to about 3, wherein the thickness ratio is the ratio of an outer diameter of the hollow cylinder to an inner diameter of the hollow cylinder.
- In some implementations, the elastomeric member includes a plurality of elastomeric ribs each having a first end connected to the first member and a second end connected to the second member.
- In certain implementations, the loudspeaker includes an enclosure, and a surround that connects the acoustic diaphragm to the enclosure. The first member can be fixed in position relative to the enclosure.
- In some implementations, at least one end of the first member is secured to the enclosure.
- In certain implementations, the surround is mounted to a frame and the frame is connected to the enclosure, and at least one end of the first member is secured to the enclosure via the frame.
- In some implementations, the oscillatory force source includes a moving magnet motor. The moving magnet motor includes an armature that is coupled to the lever and includes a permanent magnet, and a stator for creating magnetic flux for the armature to interact with, thereby to drive motion of the acoustic diaphragm.
- In certain implementations, the moving magnet motor is arranged such that magnetic crashing forces resulting from magnetic attraction between the stator and the one or more permanent magnets are substantially parallel to an axis of rotation of the lever.
- In some implementations, the moving magnet motor is arranged such that magnetic crashing forces resulting from magnetic attraction between the stator and the one or more permanent magnets are substantially perpendicular to an axis of rotation of the lever.
- In another aspect, a loudspeaker includes an acoustic diaphragm and a moving magnet motor. The moving magnet motor includes an armature comprising a permanent magnet, and a stator for creating magnetic flux for the armature to interact with, thereby to drive motion of the armature. The loudspeaker also includes a lever that couples the armature and the acoustic diaphragm to transmit motion of the armature to the acoustic diaphragm to cause the acoustic diaphragm to move, and a pivot that is coupled to lever so that motion of the armature causes the lever to move in an arcuate path about the pivot. The pivot includes a pair of elastomeric torsion bushings. Each of the elastomeric torsion bushings includes a first member, a second member that is coupled to the lever and is movable relative to the first member, and an elastomeric member that couples the first member to the second member.
- Implementations may include one of the following features, or any combination thereof.
- In some implementations, the elastomeric torsion bushings are spaced apart so as to allow the acoustic diaphragm to move therebetween.
- Implementations can provide one or more of the following advantages.
- In some implementations, the use of one or more elastomeric torsion bushings provide for a frictionless pivot for a lever arm used to drive motion of acoustic diaphragm.
- In certain implementations, the use of one or more elastomeric torsion bushings provides for a pivot that has low torsional stiffness (e.g., 0.1-1 Nm/rad).
- In some implementations, the use of one or more elastomeric torsion bushings provides for a pivot that has high radial stiffness (e.g., 200-2000 N/mm) and/or high axial stiffness (50-500 N/mm).
- Other aspects, features, and advantages are in the description, drawings, and claims.
-
FIG. 1A is a top plan view of a loudspeaker that employs an elastomeric torsion bushing for providing a pivot for a lever that drives an acoustic diaphragm. -
FIG. 1B is a cross-sectional side view of the loudspeaker ofFIG. 1A , taken alongline 1B-1B. -
FIG. 2 illustrates oscillatory, arcuate movement of the lever and pistonic movement of an acoustic diaphragm of the loudspeaker ofFIG. 1A . -
FIG. 3A is a top view of the pivot and lever ofFIG. 1A . -
FIG. 3B is a cross-sectional view of the pivot ofFIG. 3A , taken alongline 3B-3B. -
FIG. 3C is a cross-sectional view of the pivot and lever ofFIG. 3A , taken alongline 3C-3C. -
FIG. 4 is a perspective view of the pivot and lever ofFIG. 1A including an armature for a moving magnet motor. -
FIG. 5 is a perspective view of a stator for a moving magnet motor. -
FIGS. 6A , 6B, and 6C are top, end, and side views, respectively, of the pivot and lever ofFIG. 1A together with a moving magnet motor. -
FIG. 7A is a top view of the lever ofFIG. 1A with an alternative pivot arrangement. -
FIG. 7B is a cross-sectional side view of an elastomeric torsion bushing from the pivot ofFIG. 7A , taken alongline 7B-7B. -
FIG. 8A is a top plan view of another implementation of a loudspeaker that employs elastomeric torsion bushings for providing a pivot for a lever that drives an acoustic diaphragm. -
FIG. 8B is a cross-sectional side view of the loudspeaker ofFIG. 8A , taken alongline 8B-8B. -
FIG. 9 illustrates oscillatory, arcuate movement of the lever and pistonic movement of an acoustic diaphragm of the loudspeaker ofFIG. 8A . -
FIGS. 10 and 11 are end views of alternative implementations of elastomeric torsion bushings. -
FIGS. 12A and 12B are plan and perspective views, respectively, of a multi-lever loudspeaker. -
FIG. 12C is an exploded perspective view of the levers from the loudspeaker ofFIG. 12A showing details of elastomeric torsion bushings. -
FIGS. 13A and 13B are plan and perspective views, respectively, of another implementation of a multi-lever loudspeaker. -
FIG. 13C is an exploded perspective view of the levers from the loudspeaker ofFIG. 13A showing details of elastomeric torsion bushings. - Referring to
FIGS. 1A and 1B loudspeaker 100 includes an acoustic diaphragm 102 (e.g., a cone type speaker diaphragm, also known simply as a “cone”) that is mounted to anenclosure 104, which may be metal, plastic, or other suitable material, by asurround 106, which functions as a pneumatic seal and as a suspension element. For example, in some instances thesurround 106 is mounted to aframe 108 and theframe 108 is connected to theenclosure 104. Theloudspeaker 100 includes alever 110 that is mechanically connected at one point along thelever 110 to theacoustic diaphragm 102 and at another point along thelever 110 to anoscillatory force source 112. - The
lever 110 is pivotally connected to a mechanical ground reference, such as theenclosure 104 or theframe 108, via apivot 114. As illustrated inFIG. 2 , when an oscillatory force (arrow 116) is applied to thelever 110 via the oscillatory force source 112 (FIG. 1A ), thelever 110 is driven in an arcuate path (arrow 117) about thepivot 114. The motion of thelever 110 is transferred to theacoustic diaphragm 102 via the connection point, which causes theacoustic diaphragm 102 to move along a path (arrow 118) between a fully extended position and a fully retracted position. In some cases, the connection point may include aconnector 119, such as a hinge or link, which allows thelever 110 to move relative to theacoustic diaphragm 102, thereby to allow theacoustic diaphragm 102 to move in a pistonic motion (arrow 118), rather than following the arcuate path of thelever 110. - To facilitate the arcuate motion of the
lever 110, thepivot 114 includes at least one elastomeric torsion bushing.FIGS. 3A , 3B, and 3C illustrate one implementation of thepivot 114 which includes such an elastomeric torsion bushing 120. The elastomeric torsion bushing 120 provides a low cost, frictionless hinge for thelever 110. - The bushing 120 includes a first, outer (housing)
member 122; a second, inner (pin)member 124; and anelastomeric member 126 disposed therebetween. A first,inner surface 128 of theelastomeric member 126 is bonded to theinner member 124 and a second,outer surface 130 of theelastomeric member 126 is bonded to theouter member 122 such that theouter surface 130 of theelastomeric member 126 moves with theouter member 122, during rotation of thelever 110, relative to theinner surface 128. At least one of the opposing ends 136 a, 136 b of theinner member 124 is fixed to a mechanical ground reference, such as the enclosure 104 (FIG. 1A ) or the frame 108 (FIG. 1A ) and such that a longitudinal axis 138 of theinner member 124 is coincident with the axis of rotation 140 of thelever 110. Theouter member 122 is coaxial with theinner member 124 and is secured to thelever 110 such that theouter member 122 rotates with thelever 110 relative to theinner member 124. In some cases, thelever 110 and theouter member 122 may both be part of one unitary structure. - The outer and
inner members elastomeric member 126 is formed of an elastomer, such as silicone rubber, polyurethane, etc. Silicone materials may be beneficial because they tend to exhibit very good properties of creep. Silicone rubber, for example, can offer several material property benefits, such as temperature stability; low modulus; low, moderate, or high dissipation factor (tan δ) is possible; good creep resistance; fast curing using catalysts and elevated temperatures; injection moldable; and can offer very high elongation (e.g., about 900%). Theelastomeric member 126 can be formed between the outer andinner members elastomeric member 126 and the outer andinner members elastomeric member 126 forms to the shape of the space between the outer andinner members outer member 122, theinner member 124, and theelastomeric member 126 could be connected together using geometric locking. - It can be desirable to design the bushing 120 to have high axial and radial stiffness relative to rotational stiffness, while keeping strain from a given rotation below the fatigue limit of the elastomeric material. The following equations (1), (2) and (3) describe axial to rotational stiffness ratio, radial to rotational stiffness ratio and peak strain:
-
- where,
- t=thickness ratio of the elastomeric member; described by equation (4):
-
- and,
- a=inner diameter of the elastomeric member,
- b=outer diameter of the elastomeric member, and
- θ=angle of rotation (in radians) of the outer surface of the elastomeric member relative to the inner surface of the elastomeric member.
- It has been found that a thickness ratio “t” of about 1.2 to about 3 (e.g., 2) generally provides a bushing with sufficiently low peak torsional strain (e.g., less than 20%) and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm).
- Equations (1) and (2) also show that the stiffness ratios improve when the inner diameter “a” of the
elastomeric member 126 is minimized. However, it is worth noting that there are limits to how small “a” can be made. Those limits include: stiffness of theinner member 124, and shear forces between theelastomeric member 126 and theinner member 124. As the inner diameter “a” is reduced the shearing load resulting from the rotation of theouter member 122 relative to theinner member 124 acts on a diminishing surface area. The inner diameter “a” needs to be large enough to provide sufficient surface area so that the shearing load does not exceed the strength of the bond between theelastomeric member 126 and theinner member 124. -
FIGS. 4 , 5, 6A, 6B and 6C illustrate one implementation of the oscillatory force source 112 (FIG. 6A ) for applying force to thelever 110. With reference toFIG. 4 , in the illustrated implementation, theoscillatory force source 112 includes a substantiallyplanar armature 142 that is attached to thelever 110. Thearmature 142 includes one or more permanent magnets 146 (one shown). Thearmature 142 and thelever 110 may be part of one unitary structure. Referring toFIG. 5 , theoscillatory force source 112 also includes astator 148 that includes one or more cores 150 (two shown) which define anair gap 152. Thecores 150 are formed of high magnetic permeability material around which coils 154 are wound. As shown inFIGS. 6A and 6B , thelever 110 is positioned such that thearmature 142 is in theair gap 152 and electrical current is passed through the coils so that that the combination of thearmature 142, thecores 150, and thecoils 154 form a moving magnet motor. In this arrangement, the force results from the interaction of the magnetic field in the gap due to the current flowing in thecoils 154 and the magnetic field of thepermanent magnet 146, so the force is applied to thelever 110 in a non-contact manner. - Moving magnet motors can be subject to a magnetic crashing force which results from magnetic attraction between the
stator 148 andarmature 142. In the illustrated example, the crashing force is substantially in the axial direction, and varies as a function of the distance between thearmature 142 and thecores 150; the closer thepermanent magnet 146 is to thecores 150, the stronger the magnetic crashing force. It may be convenient to think of the structure as requiring a crashing stiffness that inhibits thearmature 142 from crashing into thecores 150. Here, since the magnetic crashing force is in the axial direction, the high axial stiffness of the elastomeric torsion bushing 120 can be beneficial to ensure that there is little relative motion between thearmature 142 and thecores 150 in the axial direction (as shown inFIGS. 6A and 6B ). -
FIGS. 7A and 7B illustrate another implementation of apivot 214 that can be employed, for example, in theloudspeaker 100 ofFIG. 1A and which may be particularly beneficial where the magnetic crashing forces are high in the axial direction. Thepivot 214 includes a pair of conicalelastomeric torsion bushings 220 arranged along the axis of rotation 140 of thelever 110 with ashaft member 221 extending therebetween. - Each
elastomeric torsion bushing 220 includes a first, outer (housing)member 222; a second, inner (pin)member 224; and anelastomeric member 226 disposed therebetween and bonded thereto. Afirst end 236 a of theinner member 224 is fixed to a mechanical ground reference, such as the enclosure 104 (FIG. 1A ) or the frame 108 (FIG. 1A ) and such that a longitudinal axis 238 of theinner member 224 is coincident with the axis of rotation 140 of thelever 110. Theouter member 222 is coaxial with theinner member 224 and is secured to thelever 110 such that theouter member 222 rotates with thelever 110 relative to theinner member 224. A first (inner)surface 228 of theelastomeric member 226 is bonded to theinner member 224 and a second (outer)surface 230 of theelastomeric member 226 is bonded to theouter member 222 such that thesecond surface 230 moves with the outer member 222 (e.g., during rotation of the lever) relative to theinner surface 228. In some cases, thelever 110 and theouter member 222 may both be part of one unitary structure. For example, theouter members 222 can be integral with theshaft member 221, which can be integral with thelever 110. - In this implementation, the
elastomeric member 226 is in the form of frusto-cone having ahollow center region 260. The frusto-cone has an outer diameter “b” that tapers at a first taper angle α along the length of the frusto-cone and an inner diameter “a” that tapers at a second taper angle β along the length of thehollow center region 260. The first and second taper angles α, β differ, with the second taper angle β being smaller than the first taper angle α, so as to maintain a substantially constant thickness ratio “t” of theelastomeric member 226 along the length of thehollow center region 260. The thickness ratio “t” is the ratio of the outer diameter “b” over the inner diameter ‘a.’ It has been found that a thickness ratio “t” of about 1.2 to about 3 generally provides a bushing with sufficiently low peak strain and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm). - The
outer member 222 includes atapered recess 262 within which theelastomeric member 226 is disposed. Thetapered recess 262 tapers at the first taper angle α so that theouter surface 230 of theelastomeric member 226 conforms to the shape of the taperedrecess 262 allowing for an intimate bond between theelastomeric member 226 and theouter member 222. Theinner member 224 includes a tapered end portion 264 that is received within thehollow center region 260 of theelastomeric member 226. The tapered end portion 264 tapers at the second taper angle β so that theinner surface 228 of theelastomeric member 226 conforms to the shape of the tapered end portion 264 allowing for an intimate bond between theelastomeric member 226 and theinner member 224. The introduction of these tapered surfaces along the axial direction of thepivot 214 allow for compression of theelastomeric member 226 between the tapered surfaces of the outer andinner members elastomeric member 226 can assist the shear strength of the bonds between theelastomeric member 226 and the outer andinner members - Other Implementations
-
FIGS. 8A and 8B illustrate another example of aloudspeaker 300 that includes anacoustic diaphragm 302 that is mounted to anenclosure 304 by asurround 306. In the illustrated example, thesurround 306 is mounted to aframe 308 and theframe 308 is connected to theenclosure 304. Alever 310 couples anarmature 342 to theacoustic diaphragm 302 for transmitting motion of thearmature 342 to theacoustic diaphragm 302. - The
armature 342 includes one or more permanent magnets 346 (one shown,FIG. 8B ). Thearmature 342 is driven by a stator 348, which provides a magnetic flux for the one or morepermanent magnets 346 to interact with, thereby to drive motion of the acoustic diaphragm. The stator 348 that includes one or more cores 350 (two shown) which define anair gap 352. Thecores 350 are formed of high magnetic permeability material around which coils 354 are wound. Thelever 310 is positioned such that thearmature 342 is in theair gap 352 and electrical current is passed through the coils so that that the combination of thearmature 342, thecores 350, and thecoils 354 form a moving magnet motor 312. In this arrangement, the force results from the interaction of the magnetic field in the gap due to the current flowing in thecoils 354 and the magnetic field of thepermanent magnet 346, so the force is applied to thelever 310 in a non-contact manner. - The
lever 310 is pivotally connected to a mechanical ground reference, such as theenclosure 304 or theframe 308 of theloudspeaker 300, at apivot 314 such that thelever 310 moves in an arcuate path. Thelever 310 includes a pair ofsupport arms 360 that are fixed to thepivot 314 and support thearmature 342. A cross-member 362 connects thesupport arms 360 to alever arm 364. Thelever arm 364 is connected to theacoustic diaphragm 302 via a connector 319, such as a hinge, which allows thelever 310 to move relative to theacoustic diaphragm 302, thereby to allow theacoustic diaphragm 302 to move in a pistonic motion, rather than following the arcuate path of thelever 310. - The
pivot 314 includes a pair ofelastomeric torsion bushings 320 which are connected to each other via thecross-member 362 of thelever 310. In the illustrated example, each of thebushings 320 includes an inner (pin)member 324 that includes afirst end 336 a that is fixed to a mechanical ground reference, such as theenclosure 304 or theframe 308 of theloudspeaker 300; and a second,free end 336 b opposite thefirst end 336 a. Anelastomeric member 326 circumferentially surrounds and is bonded to theinner member 324. An outer (housing)member 322 circumferentially surrounds and is bonded to theelastomeric member 326. As in the examples discussed above, theelastomeric member 326 is formed of an elastomer and can have a thickness ratio “t” of about 1.2 to about 3. - Referring now to
FIG. 9 , thelever 310, in combination with the interaction between thearmature 342 and the stator 348 (not shown inFIG. 9 ), moves theacoustic diaphragm 302 in a pistonic motion (as indicated by arrow 318). Notably, thebushings 320 are spaced apart from each other and the cross-member 362 (FIG. 8A ) is offset from thebushings 320 such that the diaphragm is free to move therebetween, e.g., during a retraction. - Also worth noting is that in the implementation illustrated in
FIGS. 8A , 8B, and 9, the moving magnet motor is arranged such that magnetic crashing forces resulting from interaction between the stator and the one or morepermanent magnets 346 are substantially in the radial direction and perpendicular to the axis of rotation of the lever. In this regard, the high radial stiffness offered by theelastomeric torsion bushings 320 can be particularly beneficial to inhibit crashing. - In some implementations, a frusto-cone bushing, such as illustrated in
FIG. 7B , may also be used with the motor implementation ofFIGS. 8A and 8B . -
FIG. 10 illustrates another implementation of anelastomeric torsion bushing 420 that can be utilized, for example, in the pivots in the loudspeakers described above. Thebushing 420 includes apivot shaft 424. A plurality ofelastomeric ribs 426 connect thepivot shaft 424 to arigid housing 422 such that therigid housing 422 can rotate relative to thepivot shaft 424. Each of theribs 426 includes a first end that is bonded to thepivot shaft 424 and a second end that is bonded to and moves with therigid housing 422. - In some cases, the
pivot shaft 424 can have at least one of its ends fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and therigid housing 422 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker. - Alternatively, the
rigid housing 422 can be fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and thepivot shaft 424 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker. -
FIG. 11 illustrate yet another implementation of anelastomeric torsion bushing 520 that can be utilized in the pivots of the loudspeakers described above. Thebushing 520 includes apivot shaft 524. A pair ofelastomeric ribs 526 connects thepivot shaft 524 to arigid housing 522. Thepivot shaft 524 can have at least one of its ends fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and therigid housing 522 can be secured to a lever used for driving an acoustic diaphragm of a loudspeaker. Therigid housing 522 can rotate relative to thepivot shaft 524. Each of theribs 526 includes a first end that is bonded to thepivot shaft 524 and a second end that is bonded to and moves with therigid housing 522. In the implementation ofFIG. 11 , thehousing 522 only partially surrounds thepivot shaft 524. - Alternatively, the
rigid housing 522 can be fixed to a mechanical ground reference, such as an enclosure or a frame of a loudspeaker, and thepivot shaft 524 can be secured to a lever used for driving an acoustic diaphragm of the loudspeaker. - While an oscillatory force source in the form of a moving magnet motor has been described, the oscillatory force may instead be applied with a moving coil motor in which a coil wound on a bobbin moves with the lever. The motor also includes a stationary permanent magnet and a stator defining an air gap, in which the bobbin moves. Electrical current is passed through the coil so that that the combination of the magnet, core, and coil form a moving coil motor. Force results from interaction of a magnetic field due to the current flowing in the coil and a magnetic field from the stationary permanent magnet so the force is applied to the lever in a non-contact manner. Alternatively, the oscillatory force may be applied mechanically, for example, by connecting the lever to a linear actuator.
- Although implementations have been described which include a single lever for driving motion of an acoustic diaphragm, multi-lever configurations are also possible. For example,
FIGS. 12A and 12B are plan and perspective views, respectively, of an implementation of aloudspeaker 600 that includes plural levers 610 (two shown).FIG. 12C is an exploded perspective view of thelevers 610 from the loudspeaker ofFIG. 12A showing the details of thepivots 620. - In the implementation illustrated in
FIGS. 12A through 12C , thelevers 610 are configured to rotate aboutrespective pivots 614. Thepivots 614 are arranged inboard of a pair ofarmatures 642, each of thearmatures 642 being associated with a corresponding one of thelevers 610. - In the illustrated example, an
acoustic diaphragm 602 is mounted to anframe 608 by a surround 606. The surround 606 is mounted to theframe 608 and the frame 208 can be connected to an enclosure (not shown). Thelevers 610 couple thearmatures 642 to theacoustic diaphragm 602 for transmitting motions of thearmatures 642 to theacoustic diaphragm 602. - Each of the
armatures 642 includes a permanent magnet 646 (FIG. 12C ), and eacharmature 642 is driven by an associatedstator 648. Thestators 648 provide magnetic flux for thepermanent magnets 646 to interact with, thereby to drive motion of theacoustic diaphragm 602. Each of thestators 648 includes a pair ofcores 650, which together define an air gap within which an associated one of thearmatures 642 is disposed. Thecores 650 can be secured to the frame 608 (e.g., with an adhesive). - Each
core 650 includes acoil 654 of electrically conductive material wound about it. Current incoils 654 produce magnetic flux across the air gaps. The magnetic flux interacts with thepermanent magnets 646 of thearmatures 642 to drive the motion of theacoustic diaphragm 602. - Each
lever 610 includes a pair ofsupport arms 660 that support thearmature 642. A cross-member 662 connects thesupport arms 660 to alever arm 664. Eachlever arm 664 is connected to theacoustic diaphragm 602 viaconnector 619, such as a hinge or flexure, which allows thelevers 610 to move relative to theacoustic diaphragm 602, thereby to allow theacoustic diaphragm 602 to move in a pistonic motion, rather than following the arcuate path of thelevers 610. - Referring to
FIG. 12C , thepivots 614 each include a pair ofelastomeric torsion bushings 620 which are connected to each other via thecross-member 662 of the corresponding one of thelevers 610. In the illustrated example, each of thebushings 620 includes an inner (pin)member 624 that includes afirst end 636 a that is fixed to a mechanical ground reference, such as theframe 608 of theloudspeaker 600; and a second,free end 636 b opposite thefirst end 636 a. Anelastomeric member 626 circumferentially surrounds and is bonded to theinner member 624. An outer (housing)member 622 circumferentially surrounds and is bonded to theelastomeric member 626. As in the examples discussed above, theelastomeric member 626 is formed of an elastomer and can have a thickness ratio “t” of about 1.2 to about 3.FIGS. 13A , 13B, and 13C illustrate another implementation of a multi-lever loudspeaker that utilizes the conical elastomeric torsion bushings ofFIG. 7A . Referring toFIGS. 13A and 13B , theloudspeaker 700, includes a mechanical load, in this example an acoustic diaphragm 702 (e.g., a cone type speaker diaphragm, also known simply as a “cone”), that is mounted to aframe 708 via asurround 706. Theframe 608 may be secured to an enclosure (not shown). Theloudspeaker 700 also includes a pair oflevers 710 each of which couples an associatedarmature 742 to theacoustic diaphragm 602 for transmitting motion of thearmatures 742 to theacoustic diaphragm 602 to cause theacoustic diaphragm 602 to move, relative to theframe 708. - Notably, in the implementation shown in
FIGS. 13A through 13C both of thearmatures 742 are driven by a single,common stator 748, which provides a magnetic flux for the permanent magnets 746 (FIG. 13C ) of both of thearmatures 742 to interact with, thereby to drive motion of theacoustic diaphragm 702. - The
stator 748 can include a pair ofU-shapes cores 750 of high magnetic permeability material, such as soft iron. Eachcore 750 includes acoil 754 of electrically conductive material wound about it. Thecores 750 are arranged adjacent to each other and define an air gap therebetween, which is substantially filled by thearmatures 742. The air gap is a single, common air gap that is shared by botharmatures 742. - Current in
coils 754 produces a magnetic flux across the air gap. The magnetic flux interacts with thepermanent magnets 746 of thearmatures 742 to drive the motion of theacoustic diaphragm 702. The combination of thearmatures 742, thecores 750, and thecoils 754 form a moving magnet motor. The interaction of the magnetic field in the air gap due to current flowing in thecoils 754 and magnetic fields of themagnets 746 apply force to themagnets 746 in a non-contact manner. Force from themagnets 746 is coupled structurally to thelevers 710 and ultimately to theacoustic diaphragm 702. - Each of the
levers 710 is pivotally connected to a mechanical ground reference, such as theframe 108 of theloudspeaker 100, such that thelevers 710 each move in an arcuate path aboutrespective pivots 714. Thearmatures 742 and thestator 748 are positioned beneath theacoustic diaphragm 702 with thepivots 714 being arranged outboard of thearmatures 742. That is, thearmatures 742 are disposed between thepivots 714 of thelevers 710. - Referring to
FIG. 13C , thepivots 714 each include a pair of conicalelastomeric torsion bushings 720 arranged along the axis of rotation of the associatedlever 710 with ashaft member 721 extending therebetween. - Each
elastomeric torsion bushing 720 includes a first, outer (housing)member 722; a second, inner (pin)member 724; and anelastomeric member 726 disposed therebetween and bonded thereto. A first end of theinner member 724 is fixed to a mechanical ground reference, such as the frame 708 (FIG. 13A ) and such that a longitudinal axis of theinner member 724 is coincident with the axis of rotation of thelever 710. Theouter member 722 is coaxial with theinner member 724 and is secured to thelever 710 such that theouter member 722 rotates with thelever 710 relative to theinner member 724. A first (inner)surface 728 of theelastomeric member 726 is bonded to theinner member 724 and a second (outer)surface 730 of theelastomeric member 726 is bonded to theouter member 722 such that thesecond surface 730 moves with the outer member 722 (e.g., during rotation of the lever) relative to theinner surface 728. In some cases, thelever 710 and theouter member 722 may both be part of one unitary structure. For example, theouter members 722 can be integral with theshaft member 721, which can be integral with thelever 710. - In this implementation, the
elastomeric member 726 is in the form of frusto-cone having ahollow center region 760. The frusto-cone has an outer diameter “b” that tapers at a first taper angle along the length of the frusto-cone and an inner diameter “a” that tapers at a second taper angle along the length of thehollow center region 760. The first and second taper angles differ, with the second taper angle being smaller than the first taper angle, so as to maintain a substantially constant thickness ratio “t” of theelastomeric member 726 along the length of thehollow center region 760. The thickness ratio “t” is the ratio of the outer diameter “b” over the inner diameter “a.” It has been found that a thickness ratio “t” of about 1.2 to about 3 generally provides a bushing with sufficiently low peak strain and torsional stiffness (e.g., 0.1-1 Nm/rad), and sufficiently high axial stiffness (e.g., 50-500 N/mm) and radial stiffness (e.g., 200-2000 N/mm). - The
outer member 722 includes atapered recess 762 within which theelastomeric member 726 is disposed. Thetapered recess 762 tapers at the first taper angle α so that theouter surface 730 of theelastomeric member 726 conforms to the shape of the taperedrecess 762 allowing for an intimate bond between theelastomeric member 726 and theouter member 722. Theinner member 724 includes atapered end portion 764 that is received within thehollow center region 760 of theelastomeric member 726. Thetapered end portion 764 tapers at the second taper angle so that theinner surface 728 of theelastomeric member 726 conforms to the shape of thetapered end portion 764 allowing for an intimate bond between theelastomeric member 726 and theinner member 724. The introduction of these tapered surfaces along the axial direction of thepivot 714 allow for compression of theelastomeric member 726 between the tapered surfaces of the outer andinner members elastomeric member 726 can assist the shear strength of the bonds between theelastomeric member 726 and the outer andinner members - A number of implementations have been described. Nevertheless, it will be understood that additional modifications may be made without departing from the spirit and scope of the inventive concepts described herein, and, accordingly, other implementations are within the scope of the following claims.
Claims (20)
Priority Applications (2)
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US14/200,614 US9357279B2 (en) | 2014-03-07 | 2014-03-07 | Elastomeric torsion bushings for levered loudspeakers |
PCT/US2015/018699 WO2015134584A1 (en) | 2014-03-07 | 2015-03-04 | Elastomeric torsion bushings for levered loudspeakers |
Applications Claiming Priority (1)
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US14/200,614 US9357279B2 (en) | 2014-03-07 | 2014-03-07 | Elastomeric torsion bushings for levered loudspeakers |
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US20150256911A1 true US20150256911A1 (en) | 2015-09-10 |
US9357279B2 US9357279B2 (en) | 2016-05-31 |
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US14/200,614 Active 2034-06-06 US9357279B2 (en) | 2014-03-07 | 2014-03-07 | Elastomeric torsion bushings for levered loudspeakers |
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WO (1) | WO2015134584A1 (en) |
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CN106851507A (en) * | 2017-03-03 | 2017-06-13 | 万魔声学科技有限公司 | Audio unit and its audio driven mechanism |
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US10154347B2 (en) | 2015-10-23 | 2018-12-11 | Bose Corporation | Bushings constrained by compression in levered apparatus |
IT202100032906A1 (en) * | 2021-12-29 | 2023-06-29 | Powersoft S P A | SOUND SPEAKER AND METHOD FOR EXTENDING THE LOW FREQUENCY RESPONSE OF AN ACOUSTIC SPEAKER. |
IT202100032897A1 (en) * | 2021-12-29 | 2023-06-29 | Powersoft S P A | TRANSDUCER FOR A SOUND SPEAKER AND METHOD FOR PRODUCING THE TRANSDUCER. |
EP4207809A1 (en) | 2021-12-29 | 2023-07-05 | Powersoft SpA | Sound diffuser and a method for diffusing a sound through a sound diffuser |
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IT202100032906A1 (en) * | 2021-12-29 | 2023-06-29 | Powersoft S P A | SOUND SPEAKER AND METHOD FOR EXTENDING THE LOW FREQUENCY RESPONSE OF AN ACOUSTIC SPEAKER. |
IT202100032897A1 (en) * | 2021-12-29 | 2023-06-29 | Powersoft S P A | TRANSDUCER FOR A SOUND SPEAKER AND METHOD FOR PRODUCING THE TRANSDUCER. |
EP4207809A1 (en) | 2021-12-29 | 2023-07-05 | Powersoft SpA | Sound diffuser and a method for diffusing a sound through a sound diffuser |
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WO2015134584A1 (en) | 2015-09-11 |
US9357279B2 (en) | 2016-05-31 |
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